WO2013161880A1 - 車輪用軸受装置 - Google Patents

車輪用軸受装置 Download PDF

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Publication number
WO2013161880A1
WO2013161880A1 PCT/JP2013/062083 JP2013062083W WO2013161880A1 WO 2013161880 A1 WO2013161880 A1 WO 2013161880A1 JP 2013062083 W JP2013062083 W JP 2013062083W WO 2013161880 A1 WO2013161880 A1 WO 2013161880A1
Authority
WO
WIPO (PCT)
Prior art keywords
wheel
wheel bearing
joint member
fitting
bearing device
Prior art date
Application number
PCT/JP2013/062083
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
修二 持永
乗松　孝幸
Original Assignee
Ntn株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority to JP2012103578A priority Critical patent/JP5829173B2/ja
Priority claimed from JP2012106684A external-priority patent/JP6261846B2/ja
Priority claimed from JP2012106691A external-priority patent/JP6261847B2/ja
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Priority to US14/396,263 priority patent/US9829048B2/en
Priority to EP13782148.4A priority patent/EP2857224B1/en
Priority to CN201380022003.9A priority patent/CN104271358B/zh
Publication of WO2013161880A1 publication Critical patent/WO2013161880A1/ja

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/06—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end
    • F16D1/064—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable
    • F16D1/072—Couplings for rigidly connecting two coaxial shafts or other movable machine elements for attachment of a member on a shaft or on a shaft-end non-disconnectable involving plastic deformation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0005—Hubs with ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0015—Hubs for driven wheels
    • B60B27/0021—Hubs for driven wheels characterised by torque transmission means from drive axle
    • B60B27/0026—Hubs for driven wheels characterised by torque transmission means from drive axle of the radial type, e.g. splined key
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0015—Hubs for driven wheels
    • B60B27/0036—Hubs for driven wheels comprising homokinetic joints
    • B60B27/0042—Hubs for driven wheels comprising homokinetic joints characterised by the fixation of the homokinetic joint to the hub
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B60B27/0094—Hubs one or more of the bearing races are formed by the hub
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • F16C35/0635—Fixing them on the shaft the bore of the inner ring being of special non-cylindrical shape which co-operates with a complementary shape on the shaft, e.g. teeth, polygonal sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D1/108—Quick-acting couplings in which the parts are connected by simply bringing them together axially having retaining means rotating with the coupling and acting by interengaging parts, i.e. positive coupling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/10—Type
    • B60B2380/12—Ball bearings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2380/00—Bearings
    • B60B2380/70—Arrangements
    • B60B2380/73—Double track
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2900/00—Purpose of invention
    • B60B2900/10—Reduction of
    • B60B2900/113—Production or maintenance time
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B2900/00—Purpose of invention
    • B60B2900/20—Avoidance of
    • B60B2900/212—Damage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/60—Positive connections with threaded parts, e.g. bolt and nut connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
    • F16C2226/50—Positive connections
    • F16C2226/80—Positive connections with splines, serrations or similar profiles to prevent movement between joined parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/581—Raceways; Race rings integral with other parts, e.g. with housings or machine elements such as shafts or gear wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D1/00—Couplings for rigidly connecting two coaxial shafts or other movable machine elements
    • F16D1/10—Quick-acting couplings in which the parts are connected by simply bringing them together axially
    • F16D2001/103—Quick-acting couplings in which the parts are connected by simply bringing them together axially the torque is transmitted via splined connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/16—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts
    • F16D3/20—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members
    • F16D3/22—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts
    • F16D3/223—Universal joints in which flexibility is produced by means of pivots or sliding or rolling connecting parts one coupling part entering a sleeve of the other coupling part and connected thereto by sliding or rolling members the rolling members being balls, rollers, or the like, guided in grooves or sockets in both coupling parts the rolling members being guided in grooves in both coupling parts
    • F16D2003/22326—Attachments to the outer joint member, i.e. attachments to the exterior of the outer joint member or to the shaft of the outer joint member

Definitions

  • the present invention relates to a wheel bearing device that rotatably supports driving wheels (front wheels of FF vehicles, rear wheels of FR vehicles, all wheels of 4WD vehicles), for example, with respect to an automobile suspension.
  • the wheel bearing device disclosed in Patent Document 1 includes a wheel bearing 120 including a hub wheel 101, an inner ring 102, double row rolling elements 103 and 104, and an outer ring 105, and a fixed constant velocity.
  • the main part is composed of the universal joint 106.
  • the hub wheel 101 has an inner raceway surface 107 on the outboard side formed on the outer peripheral surface thereof, and a wheel mounting flange 109 for mounting a wheel (not shown). Hub bolts 110 for fixing the wheel disc are implanted at equal intervals in the circumferential direction of the wheel mounting flange 109.
  • An inner ring 102 is fitted to a small diameter step portion 112 formed on the inboard side outer peripheral surface of the hub wheel 101, and an inner raceway surface 108 on the inboard side is formed on the outer peripheral surface of the inner ring 102.
  • the inner ring 102 is press-fitted with an appropriate tightening allowance to prevent creep.
  • An outboard-side inner raceway surface 107 formed on the outer peripheral surface of the hub wheel 101 and an inboard-side inner raceway surface 108 formed on the outer peripheral surface of the inner ring 102 constitute a double-row raceway surface.
  • the inner ring 102 is press-fitted into the small-diameter step portion 112 of the hub wheel 101, and the end portion of the small-diameter step portion 112 is crimped to the outside, so that the inner ring 102 is prevented from coming off by the crimping portion 111 and integrated with the hub wheel 101.
  • the preload is applied to the wheel bearing 120.
  • the outer ring 105 is formed with double row outer raceway surfaces 113 and 114 facing the inner raceway surfaces 107 and 108 of the hub wheel 101 and the inner ring 102 on the inner peripheral surface.
  • the wheel bearing device is attached to the vehicle body by fitting and fixing the outer peripheral surface of the outer ring 105 to a knuckle extending from a suspension device (not shown) of the vehicle body.
  • the wheel bearing 120 has a double-row angular contact ball bearing structure, and has inner raceway surfaces 107 and 108 formed on the outer peripheral surfaces of the hub wheel 101 and the inner ring 102, and an outer raceway surface 113 formed on the inner peripheral surface of the outer ring 105.
  • the rolling elements 103 and 104 are interposed between the rolling elements 103 and 104, and the rolling elements 103 and 104 in each row are supported by the cages 115 and 116 at equal intervals in the circumferential direction.
  • a pair of seals 117, 118 that seal the annular space between the outer ring 105, the hub ring 101, and the inner ring 102 are provided at both end openings of the wheel bearing 120 so as to be in sliding contact with the outer peripheral surfaces of the hub ring 101 and the inner ring 102.
  • 105 is fitted to the inner diameters at both ends, and prevents leakage of grease filled in the inside and intrusion of water and foreign matters from the outside.
  • the constant velocity universal joint 106 is provided at one end of an intermediate shaft 122 that constitutes the drive shaft 121, and is opposed to the outer joint member 124 in which the track groove 123 is formed on the inner peripheral surface, and the track groove 123 of the outer joint member 124.
  • An inner joint member 126 having a track groove 125 formed on the outer peripheral surface, a ball 127 incorporated between the track groove 123 of the outer joint member 124 and the track groove 125 of the inner joint member 126, and the outer joint member 124.
  • the cage 128 is interposed between the inner peripheral surface and the outer peripheral surface of the inner joint member 126 and holds the ball 127.
  • the outer joint member 124 is composed of a mouse part 129 that houses internal parts composed of the inner joint member 126, the ball 127, and the cage 128, and a stem part 130 that extends integrally from the mouse part 129 in the axial direction.
  • the inner joint member 126 is coupled so that torque can be transmitted by spline fitting with the shaft end of the intermediate shaft 122 press-fitted.
  • a resin bellows for preventing leakage of a lubricant such as grease sealed inside the joint and preventing foreign matter from entering from the outside of the joint.
  • the outer boot member 124 is closed by the boot 131 and the outer joint member 124 is closed.
  • the boot 131 includes a large-diameter end portion 133 fastened and fixed to the outer peripheral surface of the outer joint member 124 by a boot band 132, a small-diameter end portion 135 fastened and fixed to the outer peripheral surface of the intermediate shaft 122 by a boot band 134,
  • the diameter end portion 133 and the small diameter end portion 135 are connected to each other, and a flexible bellows portion 136 having a diameter reduced from the large diameter end portion 133 toward the small diameter end portion 135 is formed.
  • FIG. 12 shows a state before the stem portion 130 of the outer joint member 124 is press-fitted into the shaft hole 138 of the hub wheel 101.
  • the stem portion 130 of the outer joint member 124 has a male spline formed of a plurality of convex portions 137 extending in the axial direction on the outer peripheral surface thereof.
  • the shaft hole 138 of the hub wheel 101 forms a simple cylindrical portion 139 in which a female spline is not formed on the inner peripheral surface thereof.
  • FIG. 13 shows a state after the stem portion 130 of the outer joint member 124 is press-fitted into the shaft hole 138 of the hub wheel 101.
  • the stem portion 130 of the outer joint member 124 is press-fitted into the shaft hole 138 of the hub wheel 101, and the convex portion 137 of the stem portion 130 is transferred to the inner peripheral surface of the shaft hole 138 of the hub wheel 101.
  • a concave portion 140 is formed on the inner peripheral surface of the shaft hole 138 of the hub wheel 101 so as to be in close contact with the convex portion 137 with an allowance.
  • the female screw formed at the shaft end of the stem portion 130 of the outer joint member 124 is fixed to the hub wheel 101 by screwing the bolt 142 to 141 and tightening the bolt 142 in a state where the bolt 142 is locked to the end surface of the hub wheel 101.
  • the fixed constant velocity universal joint 106 coupled to the wheel bearing 120 including the hub wheel 101, the inner ring 102, the double row rolling elements 103 and 104, and the outer ring 105 is provided on the drive shaft 121.
  • a drive shaft 121 that transmits power from an automobile engine to a wheel needs to cope with an angular displacement and an axial displacement due to a change in the relative positional relationship between the engine and the wheel.
  • a structure connected by a shaft 122 is provided.
  • the inner peripheral surface of the shaft hole 138 of the hub wheel 101 forms a simple cylindrical portion 139 in which no female spline is formed.
  • a large press-fitting load is required to transfer the convex portion 137 of the stem portion 130 to the inner peripheral surface of the shaft hole 138.
  • the tightening margin is within a range ⁇ (range from the central part of the chevron of the convex part 137 to the top of the chevron) where the concave part 140 of the shaft hole 138 and the convex part 137 of the stem part 130 are in close contact.
  • the current situation is that the wheel bearing device must be assembled to the vehicle body with the constant velocity universal joint 106 of the drive shaft 121 assembled to the wheel bearing 120.
  • the wheel bearing 120 and the constant velocity universal joint 106 of the drive shaft 121 are coupled, that is, the two constant velocity universal joints 106 of the wheel bearing 120 and the drive shaft 121 are combined.
  • , 151 are integrated with each other. Since the minimum inner diameter of the knuckle 152 (see FIG. 14) extending from the suspension device of the vehicle body is larger than the maximum outer diameter of the constant velocity universal joints 106 and 151, the assembly to the vehicle body is shown in FIGS. 15, the sliding constant velocity universal joint 151 and the fixed constant velocity universal joint 106 of the drive shaft 121 are sequentially passed through the knuckle 152 extending from the suspension device of the vehicle body, and then the outer ring of the wheel bearing 120. 105 is fitted to the knuckle 152 and fixed.
  • the drive shaft 121 is a long assembly body that connects the wheel side and the engine side, as described above, the sliding constant velocity universal joint 151 and the fixed constant velocity universal joint 106 of the drive shaft 121 are knuckled.
  • the assembling method to the vehicle body that is sequentially passed through 152 is inferior in workability, and there is a possibility that parts constituting the drive shaft 121 may be damaged during the assembling.
  • the present invention has been proposed in view of the above-mentioned problems, and the object of the present invention is to improve the workability in assembling the vehicle body and prevent damage to the components during the assembly. It is to provide a bearing device for use.
  • the present invention comprises an outer member having a double-row outer raceway surface formed on the inner periphery, and a double-row inner raceway surface facing the outer raceway surface on the outer periphery.
  • a wheel bearing comprising: an inner member comprising a hub ring and an inner ring; and a double row rolling element interposed between the outer raceway surface of the outer member and the inner raceway surface of the inner member.
  • only the circumferential side wall portion of the convex portion means a portion excluding the radial front end portion of the convex portion.
  • the recessed part which has a fastening margin only with respect to the circumferential direction side wall part of a convex part is easy to implement
  • a plurality of convex portions extending in the axial direction are formed on one of the hub portion and the stem portion of the outer joint member, and the other side has a tightening margin only on the circumferential side wall portion of the convex portion.
  • a recess is formed in advance.
  • the concave portion is formed in advance with respect to the convex portion, the convex portion and the concave portion are brought into close contact with each other as compared with the conventional case where the convex portion is transferred to a simple cylindrical portion. Therefore, the press-fit load can be reduced. Furthermore, since it is set so as to have a tightening margin only for the circumferential side wall portion of the convex portion, the press-fit load can be further reduced as compared with the case where the radial tip portion of the convex portion is included as in the prior art. Can do. As a result, after attaching the wheel bearing to the vehicle body, the outer joint member can be press-fitted into the hub wheel of the wheel bearing so that the constant velocity universal joint can be coupled to the wheel bearing, thereby improving workability.
  • the surface hardness of the convex portion is made larger than the surface hardness of the concave portion. In this way, when one of the hub wheel and the stem portion of the outer joint member is press-fitted into the other, the shape of the convex portion is easily transferred to the concave portion forming surface on the other side by plastic deformation and cutting. can do.
  • the module in the concave-convex fitting structure of the present invention is defined in the range of 0.3 to 0.75.
  • torque transmission between the hub wheel of the wheel bearing and the stem portion of the outer joint member of the constant velocity universal joint is performed.
  • a sufficient capacity can be secured, and the press-fit load when one of the hub wheel and the stem portion of the outer joint member is press-fitted into the other can be reliably reduced. It becomes easy to couple to the bearing and workability can be improved.
  • the ratio of the pitch circle diameter to the fitting length in the concave-convex fitting structure of the present invention is defined in the range of 2.0 to 3.0.
  • the ratio of the pitch circle diameter to the fitting length in the concave-convex fitting structure is defined in the range of 2.0 to 3.0, either one of the hub wheel and the stem portion of the outer joint member is attached.
  • the press-fitting load when press-fitting into the other can be reliably reduced, and it becomes easy to couple the constant velocity universal joint to the wheel bearing, thereby improving workability.
  • the shear strength of the convex portion can be increased, and sufficient strength can be secured in the concave-convex fitting structure.
  • the outer joint member can be press-fitted into the hub wheel with an axial force generated by the screw tightening structure or less. In this way, when the outer joint member is press-fitted into the hub wheel of the wheel bearing after the wheel bearing is attached to the vehicle body, there is no need to prepare a dedicated jig, and the wheel bearing device is configured.
  • the constant velocity universal joint can be easily coupled to the wheel bearing with a screw tightening structure as a part.
  • the screw tightening structure in the present invention is preferably set to a tightening torque lower than the tightening torque when the outer joint member is pressed into the hub wheel. In this way, after the outer joint member is press-fitted into the hub wheel, if the screw tightening state is once loosened and set again to a tightening torque lower than the tightening torque at the time of the press-fitting, the wheel bearing and the constant velocity universal joint It is possible to optimally manage the surface pressure generated on the contact surface, and it is possible to prevent the occurrence of stick-slip noise due to a sudden slip on the contact surface.
  • the screw tightening structure includes a female screw portion formed at the shaft end of the stem portion of the outer joint member, and a male screw portion that is engaged with the female screw portion and locked to the hub wheel. Is possible.
  • the constant-velocity universal joint is fixed to the hub wheel by screwing the male screw part into the female screw part of the stem part and tightening the male screw part in a state where the male screw part is locked to the hub wheel.
  • the screw tightening structure has a structure composed of a male screw portion formed at the shaft end of the stem portion of the outer joint member and a female screw portion that is engaged with the male screw portion and locked to the hub wheel. Is possible.
  • the constant-velocity universal joint is fixed to the hub wheel by screwing the female screw portion into the male screw portion of the stem portion and tightening the female screw portion while being locked to the hub wheel.
  • the convex portion is provided in the stem portion of the outer joint member and the concave portion is provided in the hub wheel.
  • the shape of the convex portion of the stem portion is transferred onto the concave surface of the hub wheel so that the fitting contact between the convex portion and the concave portion is achieved.
  • a concave-convex fitting structure in which the entire region is in close contact can be easily configured.
  • the concave / convex fitting structure according to the present invention is preferably a structure having an accommodating portion for accommodating a protruding portion generated by the transfer of the convex shape by press-fitting. If it does in this way, the protrusion part produced by transcription
  • the concave / convex fitting structure in the present invention is preferably a structure having a guide portion for guiding the start of press-fitting. In this way, when any one of the hub wheel and the stem portion of the outer joint member is press-fitted into the other, stable press-fitting is possible, and misalignment or tilting during press-fitting can be prevented. it can.
  • a plurality of convex portions formed in one of the hub portion and the stem portion of the outer joint member and extending in the axial direction are tightened with respect to only the circumferential side wall portion of the convex portion.
  • the outer joint member can be press-fitted into the hub wheel of the wheel bearing and the constant velocity universal joint can be coupled to the wheel bearing. It is possible to improve and prevent damage to parts during assembly.
  • the wheel bearing apparatus which concerns on this invention, it is a longitudinal cross-sectional view which shows the state before attaching a constant velocity universal joint to the wheel bearing. It is a longitudinal cross-sectional view which shows the state after attaching the constant velocity universal joint to the wheel bearing of FIG. It is sectional drawing which shows the state before attaching the constant velocity universal joint of a drive shaft to the wheel bearing with which the knuckle was mounted
  • FIG. 8A It is a principal part expanded sectional view which shows the state before press-fitting the stem part of an outer joint member to the hub ring of a wheel bearing. It is sectional drawing which follows the AA line of FIG. 6A. It is a principal part expanded sectional view which shows the state in the middle of press-fitting the stem part of an outer joint member to the hub ring of a wheel bearing. It is sectional drawing which follows the BB line of FIG. 7A. It is a principal part expanded sectional view which shows the state after pressing the stem part of an outer joint member in the hub ring of the wheel bearing. It is sectional drawing which follows the CC line of FIG. 8A. FIG.
  • FIG. 2 is a cross-sectional view showing a hub wheel and a stem portion after assembling a constant velocity universal joint to the wheel bearing of FIG. 1. It is sectional drawing which shows the state after assembling
  • FIG. 12 is an enlarged vertical cross-sectional view of a main part showing a state before the stem portion of the outer joint member is press-fitted into the shaft hole of the hub wheel in the wheel bearing device of FIG. 11. In the wheel bearing device of FIG.
  • the wheel bearing device shown in FIGS. 1 and 2 includes a hub wheel 1 and an inner ring 2 which are inner members, double-row rolling elements 3 and 4, a wheel bearing 20 including an outer ring 5 and a constant velocity universal joint 6.
  • the main part is composed.
  • FIG. 1 shows a state before the constant velocity universal joint 6 is assembled to the wheel bearing 20
  • FIG. 2 shows a state after the constant velocity universal joint 6 is assembled to the wheel bearing 20.
  • the side closer to the outer side of the vehicle body is called the outboard side (left side of the drawing) and the side closer to the center is called the inboard side (right side of the drawing).
  • the hub wheel 1 has an inner raceway surface 7 on the outboard side formed on the outer peripheral surface thereof, and includes a wheel mounting flange 9 for mounting a wheel (not shown). Hub bolts 10 for fixing the wheel disc are implanted at equal intervals in the circumferential direction of the wheel mounting flange 9.
  • the inner ring 2 is fitted to the small-diameter step portion 12 formed on the inboard side outer peripheral surface of the hub wheel 1, and the inboard-side inner raceway surface 8 is formed on the outer peripheral surface of the inner ring 2.
  • the inner ring 2 is press-fitted with an appropriate tightening allowance to prevent creep.
  • the outboard side inner raceway surface 7 formed on the outer peripheral surface of the hub wheel 1 and the inboard side inner raceway surface 8 formed on the outer peripheral surface of the inner ring 2 constitute a double row raceway surface.
  • the inner ring 2 is press-fitted into the small-diameter step portion 12 of the hub wheel 1, and the end portion of the small-diameter step portion 12 is crimped outward by swing caulking to prevent the inner ring 2 from coming off with the caulking portion 11. It is integrated with the hub wheel 1 and preload is applied to the wheel bearing 20.
  • the outer ring 5 has double-row outer raceways 13 and 14 that are opposed to the raceways 7 and 8 of the hub wheel 1 and the inner race 2 on the inner circumferential surface, and is attached to a knuckle extending from a suspension device of a vehicle body (not shown).
  • a vehicle body mounting flange 19 is provided. As will be described later, the vehicle body mounting flange 19 is fitted to the knuckle 52 and fixed by a bolt 63 (see FIG. 3).
  • the wheel bearing 20 has a double-row angular ball bearing structure, and has inner raceway surfaces 7 and 8 formed on the outer peripheral surfaces of the hub wheel 1 and the inner ring 2 and an outer raceway surface 13 formed on the inner peripheral surface of the outer ring 5. 14, the rolling elements 3 and 4 are interposed, and the rolling elements 3 and 4 in each row are supported by the cages 15 and 16 at equal intervals in the circumferential direction.
  • a pair of seals 17 and 18 that seal the annular space between the outer ring 5, the hub ring 1, and the inner ring 2 are provided at both ends of the wheel bearing 20 so as to be in sliding contact with the outer peripheral surfaces of the hub ring 1 and the inner ring 2. 5 is fitted to the inner diameters of both end portions to prevent leakage of grease filled inside and entry of water and foreign matters from the outside.
  • the constant velocity universal joint 6 is provided at one end of an intermediate shaft 22 constituting the drive shaft 21 and is opposed to the outer joint member 24 having a track groove 23 formed on the inner peripheral surface thereof and the track groove 23 of the outer joint member 24.
  • An inner joint member 26 having track grooves 25 formed on the outer peripheral surface thereof, balls 27 incorporated between the track grooves 23 of the outer joint member 24 and the track grooves 25 of the inner joint member 26, and the outer joint member 24.
  • the cage 28 is interposed between the inner peripheral surface and the outer peripheral surface of the inner joint member 26 and holds the balls 27.
  • the outer joint member 24 is composed of a mouse part 29 that accommodates internal parts including the inner joint member 26, the ball 27, and the cage 28, and a stem part 30 that extends integrally from the mouse part 29 in the axial direction.
  • the inner joint member 26 is coupled so that torque can be transmitted by fitting the shaft end of the intermediate shaft 22 by spline fitting.
  • a resin bellows for preventing leakage of a lubricant such as grease enclosed in the joint and preventing foreign matter from entering from the outside of the joint.
  • the boot 31 is attached and the opening of the outer joint member 24 is closed with the boot 31.
  • the boot 31 includes a large-diameter end portion 33 fastened and fixed to the outer peripheral surface of the outer joint member 24 by a boot band 32, a small-diameter end portion 35 fastened and fixed to the outer peripheral surface of the intermediate shaft 22 by a boot band 34,
  • the diameter end portion 33 and the small diameter end portion 35 are connected to each other, and a flexible bellows portion 36 having a diameter reduced from the large diameter end portion 33 toward the small diameter end portion 35 is formed.
  • the wheel bearing device has a cylindrical fitting surface 61 formed on the outer peripheral surface of the inboard side of the stem portion 30 of the outer joint member 24, and a plurality of axially extending surfaces on the outer peripheral surface of the stem portion 30 on the outboard side.
  • a male spline composed of the convex portions 37 is formed.
  • a cylindrical fitting surface 62 is formed on the inboard side inner peripheral surface of the shaft hole 38 of the hub wheel 1, and the convex portion 37 is formed on the outboard side inner peripheral surface of the shaft hole 38.
  • a plurality of recesses 39 having a tightening margin are formed only on the circumferential side wall 43 (see FIG. 7B).
  • the above-mentioned convex part 37 is made into the trapezoidal tooth shape of a cross section, an involute tooth shape may be sufficient.
  • the stem portion 30 of the outer joint member 24 is press-fitted into the shaft hole 38 of the hub wheel 1, and the circumferential side wall of the convex portion 37 is inserted into the shaft hole 38 of the hub wheel 1, which is a recess forming surface on the other side.
  • the concave portion 40 is formed by transferring the shape of only the portion 43 (see FIG. 7B), and the concave-convex fitting structure M in which the entire fitting contact region X between the convex portion 37 and the concave portion 40 is in close contact is configured (see FIG. 2). ).
  • the material of the outer joint member 24 and the hub wheel medium carbon steel for machine structure represented by S53C and the like is suitable.
  • the screw tightening structure N includes a female screw portion 41 formed at the shaft end of the stem portion 30 of the outer joint member 24 and a bolt that is a male screw portion that is engaged with the female screw portion 41 and is locked to the hub wheel 1. 42.
  • the constant velocity universal joint 6 is fixed to the hub wheel 1 by screwing the bolt 42 into the female screw portion 41 of the stem portion 30 and tightening the bolt 42 in a state where the bolt 42 is locked to the hub wheel 1.
  • the wheel bearing 20 has a structure in which the inner ring 2 is prevented from coming off by the caulking portion 11 and is integrated with the hub wheel 1, so that it can be separated from the outer joint member 24 of the constant velocity universal joint 6. It has become.
  • the caulking portion 11 of the hub wheel 1 of the wheel bearing 20 and the shoulder portion 45 of the outer joint member 24 are in contact with each other.
  • a stick-slip sound commonly referred to as a cuckling noise
  • This stick-slip noise is generated when the rotational torque is applied from the outer joint member 24 of the constant velocity universal joint 6 to the hub wheel 1 of the wheel bearing 20 in a stationary state when the vehicle starts.
  • the rotational torque is transmitted to the wheel 1, but the caulking portion 11 and the outer joint member 24 of the hub wheel 1 are caused by the transmission torque fluctuation between the outer joint member 24 and the wheel bearing 20 and the torsion of the outer joint member 24. Abrupt slip occurs on the contact surface with the shoulder 45 of the head. This sudden slip causes stick-slip noise.
  • the tightening torque is set lower than the tightening torque when the outer joint member 24 is press-fitted into the hub wheel 1. That is, after the outer joint member 24 is press-fitted into the hub wheel 1, the screw tightening state is once loosened, and the tightening torque is set lower than the tightening torque at the time of the press-fitting.
  • the surface pressure generated on the contact surface between the caulking portion 11 of the hub wheel 1 and the shoulder portion 45 of the outer joint member 24 can be optimally managed, and stick slip caused by a sudden slip on the contact surface. Generation of sound can be prevented beforehand.
  • a fixed type constant velocity universal joint 6 coupled to a wheel bearing 20 comprising a hub wheel 1, an inner ring 2, double row rolling elements 3, 4 and an outer ring 5 is part of a drive shaft 21. It is composed.
  • the drive shaft 21 that transmits power from the engine of the automobile to the wheels needs to cope with angular displacement and axial displacement due to a change in the relative positional relationship between the engine and the wheels.
  • a structure connected by a shaft 22 is provided.
  • a cylindrical fitting surface 61 is formed on the inboard-side outer peripheral surface of the stem portion 30.
  • the cylindrical fitting surface 62 is formed on the inboard side inner peripheral surface of the shaft hole 38 of the hub wheel 1, so that the stem portion 30 is fitted to the fitting surface 62 of the shaft hole 38 of the hub wheel 1.
  • a guide portion 64 that guides the start of press-fitting is provided between the fitting surface 62 located on the inboard side of the hub wheel 1 and the concave portion 39 located on the outboard side.
  • the guide portion 64 has a concave portion 65 that is larger than the convex portion 37 of the stem portion 30 (see the enlarged portion in FIG. 1). That is, a gap m is formed between the convex portion 37 and the concave portion 65 (see FIG. 6B).
  • the circumferential dimension of the concave portion 39 is set smaller than that of the convex portion 37 so that the above-mentioned concave portion 39 has an interference n with respect to only the circumferential side wall portion 43 of the convex portion 37. Moreover, since the site
  • the outer joint member 24 can be press-fitted into the hub wheel 1 with an axial force generated by tightening the bolt 42 or less. That is, at the time of assembling a vehicle by an automobile manufacturer, the wheel bearing 20 is fixed to the knuckle 52 extending from the suspension device of the vehicle body with the bolt 63, and then the hub of the wheel bearing 20 is pulled by the pulling force by the bolt 42 of the screw tightening structure N.
  • the stem portion 30 of the outer joint member 24 of the constant velocity universal joint 6 can be easily press-fitted into the shaft hole 38 of the wheel 1, and the constant velocity universal joint 6 of the drive shaft 21 can be easily assembled to the wheel bearing 20. This makes it possible to improve workability when assembling to the vehicle body, and prevent damage to the parts during assembling.
  • the outer joint member 24 when the outer joint member 24 is press-fitted into the hub wheel 1 of the wheel bearing 20 after the wheel bearing 20 is attached to the knuckle 52 of the vehicle body, it is not necessary to prepare a dedicated jig separately.
  • the constant velocity universal joint 6 can be easily coupled to the wheel bearing 20 with the bolt 42 which is a component constituting the bearing device.
  • the bolt 42 since it is possible to press-fit by applying a relatively small pulling force equal to or less than the axial force generated by tightening the bolt 42, the pulling workability by the bolt 42 can be improved.
  • the concave portion is caused by a slight plastic deformation and cutting of the concave portion forming surface by the circumferential side wall portion 43 of the convex portion 37.
  • the shape of the circumferential side wall 43 of the convex portion 37 is transferred to the forming surface.
  • the circumferential side wall portion 43 of the convex portion 37 bites into the concave portion forming surface so that the inner diameter of the hub wheel 1 is slightly expanded, and relative movement in the axial direction of the convex portion 37 is allowed. Is done.
  • the inner diameter of the hub wheel 1 is reduced to return to the original diameter.
  • Such a low-cost and highly reliable connection does not form gaps that cause play in the radial direction and circumferential direction of the fitting portion of the stem portion 30 and the hub wheel 1, so that the entire area X of the fitting contact portion transmits rotational torque.
  • This contributes to stable torque transmission and can prevent harsh rattling noises over a long period of time. Since the fitting contact part whole area X is in close contact as described above, the strength of the torque transmission part is improved, so that the vehicle bearing device can be reduced in weight and size.
  • the surface hardness of the convex portion 37 is made larger than the surface hardness of the concave portion 39.
  • the difference between the surface hardness of the convex portion 37 and the surface hardness of the concave portion 39 is set to 20 or more in HRC.
  • the surface hardness of the convex portion 37 is preferably 50 to 65 in HRC, and the surface hardness of the concave portion 39 is preferably 10 to 30 in HRC.
  • an accommodating portion 67 that accommodates the protruding portion 66 generated by the transfer of the convex shape by press-fitting is provided (FIGS. 7A and 7B). 8A).
  • the protruding portion 66 generated by the transfer of the convex shape by press-fitting can be held in the housing portion 67, and the protruding portion 66 can be prevented from entering the vehicle outside the apparatus.
  • the removal processing of the protruding portion 66 becomes unnecessary, the work man-hours can be reduced, the workability can be improved, and the cost can be reduced.
  • the module is defined in the range of 0.3 to 0.75.
  • the module is formed on the inner peripheral surface of the convex portion 37 formed on the outer peripheral surface of the stem portion 30 of the outer joint member 24 and the shaft hole 38 of the hub wheel 1 as shown in FIGS. 8B and 9. It means a value (PCD / Z) obtained by dividing the pitch circle diameter (PCD) in the fitting structure with the concave portion 40 by the number Z (number of teeth) of the convex portion 37.
  • the module in the concavo-convex fitting structure is set to about 1.0.
  • the module is defined in the range of 0.3 to 0.75.
  • the convex portion 37 of the stem portion 30 of the outer joint member 24 and the concave portion 40 of the shaft hole 38 of the hub wheel 1 are provided. And the torque transmission capacity between the wheel bearing 20 and the constant velocity universal joint 6 can be sufficiently ensured. Further, the press-fitting load when the stem portion 30 of the outer joint member 24 is press-fitted into the shaft hole 38 of the hub wheel 1 can be reliably reduced, and the pull-in force of the bolt 42 of the screw tightening structure N can be used. The stem portion 30 of the outer joint member 24 can be easily press-fitted into the shaft hole 38.
  • the fitting margin of the concave portion 39 with respect to the convex portion 37 becomes too small, so that it is sufficient between the wheel bearing 20 and the constant velocity universal joint 6. It is difficult to ensure a sufficient torque transmission capacity.
  • the module in the concave-convex fitting structure M is larger than 0.75, the fitting margin of the concave portion 39 with respect to the convex portion 37 becomes too large, so that the stem of the outer joint member 24 is inserted into the shaft hole 38 of the hub wheel 1.
  • part whole region X. Is specified in the range of 2.0 to 3.0.
  • the ratio of the pitch circle diameter to the fitting length means a value (PCD / X) obtained by dividing the pitch circle diameter by the fitting length.
  • the ratio of the pitch circle diameter to the fitting length was set to be smaller than 1.0.
  • the ratio of the pitch circle diameter to the fitting length is specified in the range of 2.0 to 3.0.
  • the ratio of the pitch circle diameter to the fitting length in the range of 2.0 to 3.0, when the stem portion 30 of the outer joint member 24 is press-fitted into the shaft hole 38 of the hub wheel 1. Therefore, the stem portion 30 of the outer joint member 24 can be easily press-fitted into the shaft hole 38 of the hub wheel 1 with the pulling force of the bolt 42 of the screw tightening structure N. Further, the shear strength of the convex portion 37 can be made higher than the breaking strength of the stem portion 30 of the outer joint member 24, and sufficient strength can be ensured in the concave-convex fitting structure M.
  • the ratio of the pitch circle diameter to the fitting length is smaller than 2.0, the fitting length becomes too large with respect to the pitch circle diameter. It becomes difficult to lower the press-fit load when the stem portion 30 of the outer joint member 24 is press-fitted into the shaft hole 38 of the hub wheel 1, and the stem portion 30 of the outer joint member 24 is press-fitted into the shaft hole 38 of the hub wheel 1. It becomes difficult. In addition, it is difficult to reduce the size and weight of the apparatus. On the contrary, if the ratio of the pitch circle diameter to the fitting length is larger than 3.0, the fitting length becomes too small with respect to the pitch circle diameter, so that the damage strength of the stem portion 30 of the outer joint member 24 is reduced. As a result, the shear strength of the convex portion 37 becomes lower, and it becomes difficult to ensure sufficient strength in the concave-convex fitting structure M.
  • the structure in which the bolt 42 is fastened to the end surface of the hub wheel 1 by screwing the bolt 42 into the female screw portion 41 of the stem portion 30 is exemplified.
  • the nut 69 that is.
  • the constant velocity universal joint 6 is fixed to the hub wheel 1 by tightening the nut 69 in a state where the nut 69 is locked to the hub wheel 1 by screwing the nut 69 into the male screw portion 68 of the stem portion 30. become.
  • one of the double-row inner raceway surfaces 7 and 8 formed on the inner member composed of the hub wheel 1 and the inner ring 2, that is, the inner raceway surface 7 on the outboard side is connected to the hub wheel 1.
  • a drive wheel bearing device of the type (called third generation) formed on the outer periphery is illustrated, but the present invention is not limited to this, and a pair of inner rings are press-fitted into the outer periphery of the hub wheel.
  • the outboard side raceway surface 7 is formed on the outer periphery of one inner ring
  • the inboard side raceway surface 8 is formed on the outer periphery of the other inner ring (referred to as first and second generation) type of drive.
  • the present invention can also be applied to a wheel bearing device.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rolling Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)
PCT/JP2013/062083 2012-04-27 2013-04-24 車輪用軸受装置 WO2013161880A1 (ja)

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JP2012103578A JP5829173B2 (ja) 2012-04-27 2012-04-27 車輪用軸受装置の製造方法
US14/396,263 US9829048B2 (en) 2012-04-27 2013-04-24 Bearing device for wheel
EP13782148.4A EP2857224B1 (en) 2012-04-27 2013-04-24 Bearing device for wheel and manufacturing method thereof
CN201380022003.9A CN104271358B (zh) 2012-04-27 2013-04-24 车轮用轴承装置及车轮用轴承装置的制造方法

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JP2012103578A JP5829173B2 (ja) 2012-04-27 2012-04-27 車輪用軸受装置の製造方法
JP2012-106684 2012-05-08
JP2012-106691 2012-05-08
JP2012106684A JP6261846B2 (ja) 2012-05-08 2012-05-08 車輪用軸受装置および車輪用軸受装置の製造方法
JP2012106691A JP6261847B2 (ja) 2012-05-08 2012-05-08 車輪用軸受装置および車輪用軸受装置の製造方法

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CN104271358A (zh) 2015-01-07
EP2857224B1 (en) 2020-03-25
US20150321511A1 (en) 2015-11-12
EP2857224A1 (en) 2015-04-08
CN104271358B (zh) 2018-01-16
US9829048B2 (en) 2017-11-28
EP2857224A4 (en) 2017-08-23
JP5829173B2 (ja) 2015-12-09
JP2013230753A (ja) 2013-11-14

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